US10119734B2 - Cooling device with compressor cabinet heater and a control method - Google Patents

Cooling device with compressor cabinet heater and a control method Download PDF

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Publication number
US10119734B2
US10119734B2 US11/575,488 US57548805A US10119734B2 US 10119734 B2 US10119734 B2 US 10119734B2 US 57548805 A US57548805 A US 57548805A US 10119734 B2 US10119734 B2 US 10119734B2
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Prior art keywords
compressor
temperature sensor
temperature
cooling
cooling device
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Expired - Fee Related, expires
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US11/575,488
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English (en)
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US20070214813A1 (en
Inventor
Yalcin Guldali
Ertugrul Ustundag
Sabahattin Hocaoglu
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Arcelik AS
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Arcelik AS
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Assigned to ARCELIK ANONIM SIRKETI reassignment ARCELIK ANONIM SIRKETI ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GULDALI, YALCIN, HOCAOGLU, SABAHATTIN, USTUNDAG, ERTUGRUL
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/027—Condenser control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/04—Clogging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/28—Means for preventing liquid refrigerant entering into the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/29—High ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/111—Fan speed control of condenser fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2116—Temperatures of a condenser
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21174—Temperatures of an evaporator of the refrigerant at the inlet of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • F25B41/067—
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/37—Capillary tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2700/00—Means for sensing or measuring; Sensors therefor
    • F25D2700/12—Sensors measuring the inside temperature
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • Y02B30/743—

Definitions

  • This invention relates to a cooling device a control method thereof, the cooling cycle of which is improved.
  • the refrigerant in the cooling cycle is in superheated vapor phase while leaving the compressor, the refrigerant discharged in vapor phase from the compressor first changes to the liquid-vapor phase in the condenser and then to the liquid phase close to the area of the capillary tube inlet.
  • the refrigerant starts to change toliquid-vapor phase along the capillary tube with pressure reduction and reaches the evaporator in a liquid-vapor phase with a low dryness fraction.
  • the refrigerant which changes to vapor phase at the outlet of the evaporator due to absorption of the ambient heat reaches to the compressor again.
  • split type cooling devices comprising a compressor chamber including a compressor, a condenser and a fan, evaporators connected to the compressor chamber, and cooling compartments cooled by these evaporators, and wherein the compressor chamber and evaporators are positioned separately
  • the ambient temperature that the compressor chamber is exposed to, the temperature of the surroundings of the evaporators and the tubes interposed between the compressor chamber and the evaporator may be different.
  • the refrigerant in the condenser quickly changes into the liquid phase.
  • the refrigerant When the refrigerant enters the medium of the evaporator, the refrigerant again changes to vapor since the ambient temperature increases and the event named as “vapor block” takes place at the inlet of the capillary tube when the refrigerant in vapor phase blocks the capillary tube preventing the entrance of the refrigerant to the evaporator, disrupting the cooling cycle and subsequently resulting in the cessation of the cooling process.
  • the major factors affecting viscosity are temperature and solubility.
  • the effect of solubility is greater than that of temperature, particularly at lower temperatures.
  • the hardest part of the oil recycling in the cooling cycle is in the last coil of the evaporator and the suction line. Therefore in order to take advantage of the solubility effect at places where oil is most blocked, particularly at the outlet of the evaporator, return of oil to the compressor should be provided by enabling the double phased flow of the refrigerant and reducing viscosity.
  • the compressor gets devoid of oil and as a result the compressor performance decreases. Even in cases where load of the cooling compartment is low, since the compressor operating at a low rotation rate cannot reach the necessary sweeping speed, oil is blocked in the circulation line, particularly in the evaporator.
  • the object of the present invention is to design a cooling device wherein the oil accumulation is reduced and the vapor block which may take place at the inlet of capillary tubes is prevented.
  • FIG. 1 is the schematic view of a cooling device.
  • FIG. 2 is the schematic view of a kitchen where the cooling device is placed.
  • the cooling device ( 1 ) comprises one or more cooling cabinets ( 7 ) where items to be cooled are stored, a compressor ( 2 ) which enables compression of the refrigerant, a condenser ( 3 ) which by condensing enables the superheated vapor leaving the compressor ( 2 ) to change to first liquid-vapor phase then liquid phase entirely, a compressor cabinet ( 8 ) positioned separately from the cooling cabinet ( 7 ) and into which the compressor ( 2 ) and the condenser ( 3 ) are located, one or more evaporators ( 4 ) to where the condensed fluid is delivered and absorbing the heat of the medium enabling cooling of the medium, and where the refrigerant absorbs the heat and cools the cooling cabinet ( 7 ), one or more capillary tubes ( 5 ) interposed between the compressor cabinet ( 8 ) and the evaporator ( 4 ), enabling refrigerant to be pressurized and to change to the liquid phase entirely, at least two temperature sensors ( 10 , 11 ) which detect the temperature inside the
  • One of the temperature sensors ( 10 ) is positioned in the compressor cabinet ( 8 ) and/or on the condenser ( 3 ) and detects the temperature inside the compressor cabinet ( 8 ) and/or in the condenser ( 3 ), the other temperature sensor ( 11 ) is positioned in the cooling cabinet ( 7 ) and detects the temperature of the cooling cabinet ( 7 ).
  • Thermostats may be used as temperature sensors ( 10 , 11 ).
  • the temperature sensor ( 11 ) can be positioned at the inlet of the capillary tube ( 5 ) at the end of the pumping line.
  • the cooling device ( 1 ) comprises one or more valves ( 12 ) particularly solenoid valves ( 12 ) providing the directing of the fluid exiting the capillary tube ( 5 ) to the evaporators ( 4 ) consequently to the cooling cabinet ( 7 ) by opening and closing mechanically or electrically.
  • the compressor ( 2 ) compresses the refrigerant and delivers it to the condenser ( 3 ) as superheated vapor.
  • the heat of the refrigerant is released at the condenser ( 3 ) with the forced air flow created by the fan ( 9 ) and the refrigerant gradually changes to the liquid-vapor phase and then the liquid phase entirely.
  • the refrigerant fluid leaving the compressor cabinet ( 8 ) enters the capillary tube ( 5 ) and the evaporator ( 4 ) which are in a medium having a different ambient temperature value than that of the compressor cabinet ( 8 ).
  • the fan ( 9 ) in the compressor cabinet ( 8 ) is deactivated and the refrigerant fluid reaches a certain condensation temperature and pressure value.
  • the temperature values detected by the temperature sensors ( 10 , 11 ) in the compressor cabinet ( 8 ) and the cooling cabinet ( 7 ) are controlled and if the difference between the two mediums are greater than a certain value, then the heater ( 6 ) in the compressor cabinet ( 8 ) is activated.
  • the condensation temperature and consequently the pressure of the refrigerant is brought to a desired value while the refrigerant is kept in the liquid phase and the event of “vapor block” constituted by the refrigerant changing to the vapor phase entirely at the inlet of the capillary tube ( 5 ) is prevented.
  • the refrigerant passing through the capillary tube ( 5 ) with reduced temperature and pressure enters the evaporator ( 4 ) with ease and the refrigerant absorbs the heat of the cooling cabinet ( 7 ), cooling the cooling cabinet ( 7 ), and due to the absorbed heat the refrigerant fluid quickly changes to the vapor phase as it passes through the outlet or last coil of the evaporator ( 4 ).
  • the refrigerant leaving the evaporator ( 4 ) reaches the compressor ( 2 ) in vapor phase and completes one cooling cycle.
  • the temperature values detected by the temperature sensor ( 11 ) positioned at only the inlet and/or outlet of the evaporator ( 4 ) are evaluated. If the difference between the inlet and outlet of the evaporator ( 4 ) temperature values is greater than the preset values, then the refrigerant is in superheated vapor phase at the outlet of the evaporator ( 4 ), in order to start double phase flow at the evaporator ( 4 ) outlet, firstly the compressor ( 2 ) rotation rate is increased, thus increasing the compressor ( 2 ) sweeping speed of the oil in the circulation line, particularly in the evaporator ( 4 ) and at the end of this process if double phase flow can not be accomplished, the fan ( 9 ) is deactivated and then the heater ( 8 ) in the compressor cabinet ( 8 ) and/or in the condenser ( 3 ) is activated thus starting double phase flow of the refrigerant fluid at the outlet of the evaporator ( 4 ).
  • the cooling device ( 1 ) of the present invention With the cooling device ( 1 ) of the present invention, the unintentional creation of “vapor block” at the inlet of capillary tube ( 5 ) is prevented, and especially in “split” type cooling devices, by positioning the evaporators ( 4 ) and the compressor cabinet ( 8 ) comprising the compressor ( 2 ), the condenser ( 3 ) and the fan ( 9 ) at locations having different temperature values the compressor cabinet ( 8 ) is provided to be removed to a different external emplacement than that of the cooling cabinet ( 7 ). Furthermore the oil that leaks into the circulation line from the compressor ( 2 ) is allowed to return back to the compressor ( 2 ).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Sampling And Sample Adjustment (AREA)
  • Electrical Discharge Machining, Electrochemical Machining, And Combined Machining (AREA)
  • Compressor (AREA)
  • Control Of Heat Treatment Processes (AREA)
  • Heating, Cooling, Or Curing Plastics Or The Like In General (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US11/575,488 2004-11-05 2005-11-02 Cooling device with compressor cabinet heater and a control method Expired - Fee Related US10119734B2 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
TR2004/02985 2004-11-05
TR200402985 2004-11-05
PCT/IB2005/053572 WO2006048825A1 (en) 2004-11-05 2005-11-02 A cooling device and a control method

Publications (2)

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US20070214813A1 US20070214813A1 (en) 2007-09-20
US10119734B2 true US10119734B2 (en) 2018-11-06

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US (1) US10119734B2 (es)
EP (1) EP1807662B1 (es)
JP (1) JP4949258B2 (es)
CN (1) CN101057116B (es)
AT (1) ATE383555T1 (es)
DE (1) DE602005004310T2 (es)
DK (1) DK1807662T3 (es)
ES (1) ES2299096T3 (es)
TR (1) TR200702964T1 (es)
WO (1) WO2006048825A1 (es)

Cited By (3)

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US11340003B2 (en) 2018-08-14 2022-05-24 Hoffman Enclosures, Inc. Thermal monitoring for cooling systems
US11435125B2 (en) 2019-01-11 2022-09-06 Carrier Corporation Heating compressor at start-up
US11624539B2 (en) 2019-02-06 2023-04-11 Carrier Corporation Maintaining superheat conditions in a compressor

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JP5380221B2 (ja) * 2009-09-17 2014-01-08 株式会社東芝 冷蔵庫
JP5831661B1 (ja) * 2014-09-30 2015-12-09 ダイキン工業株式会社 空調機
CN105278577B (zh) * 2015-04-02 2017-10-13 爱美达（上海）热能系统有限公司 一种双相流冷却系统中的过热度检测方法
WO2019058450A1 (ja) * 2017-09-20 2019-03-28 三菱電機株式会社 冷凍機

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CN101057116B (zh) 2010-08-18
WO2006048825A1 (en) 2006-05-11
ES2299096T3 (es) 2008-05-16
ATE383555T1 (de) 2008-01-15
DE602005004310T2 (de) 2009-01-02
DK1807662T3 (da) 2008-05-26
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EP1807662A1 (en) 2007-07-18
TR200702964T1 (tr) 2007-06-21
JP4949258B2 (ja) 2012-06-06

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